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United States Patent |
6,186,759
|
Hayano
,   et al.
|
February 13, 2001
|
Helical blade type compressor and a refrigeration cycle apparatus using the
same
Abstract
A helical blade type compressor comprising a case, a cylindrical cylinder
provided in the case, a roller disposed in the cylinder, and helical
blades of uneven pitches for dividing a compression chamber so that the
volume may be gradually smaller in the axial direction between the
cylinder and roller, by revolving the cylinder and roller to move the
compression chamber in the volume decreasing direction, thereby
compressing the air, wherein at least one seal member is provided in the
roller for separating into pressure in the case and the pressure in the
compression chamber.
Inventors:
|
Hayano; Makoto (Yokohama, JP);
Sakata; Hirotsugu (Chigasaki, JP);
Morishima; Akira (Fujinomiya, JP)
|
Assignee:
|
Kabushiki Kaisha Toshiba (Kawasaki, JP)
|
Appl. No.:
|
262320 |
Filed:
|
March 4, 1999 |
Foreign Application Priority Data
| Mar 11, 1998[JP] | 10-059778 |
Current U.S. Class: |
418/220; 418/152 |
Intern'l Class: |
F01C 021/08 |
Field of Search: |
418/220,152
|
References Cited
U.S. Patent Documents
4706971 | Nov., 1987 | Schirmer | 277/215.
|
4871304 | Oct., 1989 | Iida et al. | 418/220.
|
5332377 | Jul., 1994 | Hirayama et al. | 418/220.
|
5542832 | Aug., 1996 | Sone et al. | 418/220.
|
5791193 | Aug., 1998 | Uematsu et al. | 74/467.
|
Foreign Patent Documents |
2611524 | Jul., 1984 | DE.
| |
4220830 | Jan., 1993 | DE | 418/220.
|
224862 | Dec., 1924 | EP | 418/220.
|
3-145592 | Dec., 1924 | JP | 418/220.
|
2-80863 | Mar., 1990 | JP | 418/220.
|
2-201090 | Aug., 1990 | JP | 418/220.
|
3-3993 | Jan., 1991 | JP | 418/220.
|
3-145592 | Jun., 1991 | JP | 418/220.
|
3-172595 | Jun., 1991 | JP | 418/220.
|
5-272476 | Oct., 1993 | JP | 418/220.
|
Primary Examiner: Denion; Thomas
Assistant Examiner: Trieu; Theresa
Attorney, Agent or Firm: Oblon, Spivak, McClelland, Maier & Neustadt, P.C.
Claims
What is claimed is:
1. A helical blade type compressor comprising:
a case;
a cylinder provided in the case;
a roller disposed in the cylinder; and
helical blades provided with uneven pitchers configured to provide a
compression chamber having a volume made gradually smaller in an axial
direction, said compression chamber being formed by said blades between
said cylinder and said roller and being moved in a volume decreasing
direction by relatively revolving said cylinder and said roller thereby
compressing a gas in the compression chamber,
wherein at least one seal member is provided in said roller, said seal
member including a seal ring movably inserted into an annular groove
provided in a periphery of the roller, said seal ring abutting against
said annular groove and an inner periphery of the cylinder to separate
pressure in the case and in the compression chamber.
2. A helical blade type compressor of claim 1, wherein said annular groove
and the seal ring member to be inserted in the annular groove are provided
in a plurality each.
3. A helical blade type compressor of claim 1, wherein said roller has a
flange of a large diameter, and said seal ring is held by the flange.
4. A helical blade type compressor of claim 1, wherein said roller
comprises a main body and a lid which can be divided in the portion of
said annular groove.
5. A helical blade type compressor of claim 1, wherein the inside diameter
of the cylinder inner circumference of the portion contacting with the
seal ring member is different from the inside diameter of the portion in
which said helical blade of the cylinder is disposed.
6. A helical blade type compressor of claim 1, wherein said annular ring
and the seal ring member to be inserted in the annular ring are provided
in a plurality each, and an intermediate pressure lead-in path for leading
in a compression intermediate pressure from said compression chamber is
provided in at least one position of the spaces divided by the plural seal
ring members.
7. A helical blade type compressor of claim 1, wherein said seal member is
freely inserted into an annular groove provided in the cylinder inner
circumference, and abuts against the annular groove and roller to separate
into the pressure in the case and the pressure in the compression chamber.
8. A helical blade type compressor of claim 7, wherein said cylinder is
composed of at least two or more members that can be divided in the
portion of said annular groove.
9. A helical blade type compressor of claim 7, wherein the annular groove
in which said seal ring member is fitted is divided by a receiving member
holding one end of said cylinder and the end of said roller, and said seal
ring member abuts against said cylinder and the roller to separate into
the pressure in the case and the pressure in the compression chamber.
10. A helical blade type compressor of claim 1, wherein said seal member is
inserted into the annular groove provided at the end of said roller, and
cooperates with a receiving member for holding the end of the roller to
separate into the pressure in the case and the pressure in the compression
chamber.
11. A helical blade type compressor of claim 1, wherein said seal member is
inserted in the annular groove provided in a receiving member for holding
the end face of said roller, and cooperates with the end face of the
roller to separate into the pressure in the case and the pressure in the
compression chamber.
12. A helical blade type compressor of claim 11, wherein an intermediate
pressure lead-in path is provided for leading in a compression
intermediate pressure into said seal member from said compression chamber.
13. A helical blade type compressor of claim 10, wherein said annular ring
and the seal ring member to be inserted in the annular ring are provided
in a plurality each, and an intermediate pressure lead-in path for leading
in a compression intermediate pressure from said compression chamber is
provided in at least one position of the spaces divided by the plural seal
ring members.
14. A helical blade type compressor of claim 11, wherein an intermediate
pressure lead-in path is provided for leading in a compression
intermediate pressure into said seal member from said compression chamber.
15. A helical blade type compressor of claim 11, wherein said annular ring
and the seal ring member to be inserted in the annular ring are provided
in a plurality each, and an intermediate pressure lead-in path for leading
in a compression intermediate pressure from said compression chamber is
provided in at least one position of the spaces divided by the plural seal
ring members.
16. A helical blade type compressor of claim 1, wherein said seal member
comprises a first seal ring member and a second seal ring member, the
first seal ring member is freely inserted into the annular groove provided
in the roller outer circumference, and abuts against the annular groove
and cylinder to separate into the high pressure side and low pressure
side, and the second seal ring member is inserted in the annular groove
provided at the end face of said roller, and cooperates with a receiving
member for holding the end face of the roller to separate the high
pressure and low pressure.
17. A helical blade type compressor of claim 1, wherein said seal member
has a divided portion in one position along the circumferential direction,
and is formed so as to be expanded in diameter.
18. A helical blade type compressor of claim 17, wherein at least one of
said joint faces is always positioned in the groove for the ring, along
with revolution of the roller, when the seal ring member projects to the
maximum extent from the groove for holding the seal ring.
19. A helical blade type compressor of claim 1, wherein said seal member
has a seal ring member and a spring member for thrusting the seal ring
member in the outer circumferential direction.
20. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member, and the seal ring member comprises a ring-shaped main
body, a ring side annular groove provided on the outer circumference of
the main body, and a sub-seal ring member fitted in the ring side annular
groove.
21. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member not having divided portion, and the seal ring member
comprises a ring-shaped main body, a ring side annular groove provided on
the inner circumference of the main body, and a sub-seal ring member
fitted in the ring side annular groove.
22. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member, and the seal ring member has a ring side annular
groove opened at its outer circumferential side, and the section of the
ring side annular groove is U-form or V-form, and the opening side is at
high pressure.
23. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member, and the seal ring member has a ring side annular
groove opened at its inner circumferential side, and the section of the
ring side annular groove is U-form or V-form, and the opening side is at
low pressure.
24. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member having an outer circumference, an inner circumference,
and a plane enclosing them, and said plane is composed so that the area
sliding with the member contacting with the seal ring is smaller than the
area not sliding.
25. A helical blade type compressor of claim 11, wherein the seal member
inserted in the annular groove at the end face of said roller is a seal
ring member having seal member side annular grooves at the outer
circumference and inner circumference, sub-seal ring members are inserted
in these seal member side annular grooves, and it also has an intermediate
pressure lead-in path for leading the compression intermediate pressure in
the compression chamber to the opposite side of the sliding side of the
seal ring.
26. A helical blade type compressor of claim 25, wherein a spring member is
provided at an opposite side of the sliding surface of said seal ring.
27. A helical blade type compressor of claim 1, wherein the material of the
seal member is engineering plastic (resin).
28. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member, and the inner end portion of the seal ring member to
be inserted into the cylinder is chamfered.
29. A helical blade type compressor of claim 1, wherein said seal member is
a seal ring member, and the outer end portion of the seal ring member to
be inserted into the cylinder is chamfered.
30. A refrigeration cycle apparatus using the helical blade type compressor
of claim 1, wherein the refrigerant used in the refrigeration cycle is a
refrigerant higher in condensation or evaporation pressure than R22.
31. The helical blade compressor of claim 1, wherein said gas is a
refrigerant gas used in a refrigeration cycle.
Description
BACKGROUND OF THE INVENTION
The present invention relates to a helical blade type compressor used as a
compressor for composing a refrigeration cycle of, for example, an air
conditioner.
The helical blade type compressor has been recently proposed.
In this helical blade type compressor, a cylinder for composing the
compression mechanism is disposed in an enclosed case, and a roller
revolves in the cylinder. Spiral grooves are provided in the roller
circumference or cylinder inside, and helical blades are contained to be
free to move in and out.
In such constitution, plural combustion chambers are formed continuously
between the cylinder and roller, and between mutual helical blades. When
the roller revolves in this state, the refrigerant gas is sucked into the
compression chamber at one end side, and is compressed as being gradually
transferred to the compression chamber at other end side.
According to this kind of compressor, defective sealing performance in the
conventional reciprocating type or rotary type compressor can be
eliminated, and the sealing performance is enhanced in a relatively simple
constitution, and efficient compression is realized, while it is easier to
manufacture and assemble parts.
In this helical blade type compressor, sealing between the high pressure
side and low pressure side is achieved by the sliding surface or tiny gap
between the roller and the bearing member which receives the thrust load
of the roller.
However, in the structure of sealing by making use of the thrust load of
the roller, it is hard to keep a sufficient sealing performance, and the
thrust sliding surface may be seized in case of occurrence of an excessive
thrust load. In the conventional structure, since the thrust load acting
on the roller cannot be controlled easily, there were problems to be
solved in relation to performance and reliability.
BRIEF SUMMARY OF THE INVENTION
It is hence an object of the invention to present a helical blade type
compressor capable of controlling the thrust load and obtaining a
sufficient sealing performance.
To solve the problems, the invention discloses the following constitutions,
effects and actions. The corresponding drawings are described below for
reference, but it must be noted that they should not be interpreted to
limit the scope of the invention.
(1) (corresponding to FIG. 1 and FIG. 5) A helical blade type compressor
comprising:
a case, a cylindrical cylinder provided in the case, a roller disposed in
the cylinder, and helical blades of uneven pitches for dividing a
compression chamber so that the volume may be gradually smaller in the
axial direction between the cylinder and roller, for revolving the
cylinder and roller to move the compression chamber in the volume
decreasing direction, thereby compressing the air,
in which at least one seal member is provided in the roller for separating
into pressure in the case and the pressure in the compression chamber.
According to such constitution, by disposing the seal member for separating
high and low pressure in the cylinder, secure sealing is enabled without
generating excessive thrust load, and the performance and reliability are
enhanced. By the use of seal ring, it is easy to adjust the thrust load
acting on the roller.
In this constitution, the expressing "provided in the roller" means not
only direct holding by the roller, but also contacting with the roller as
being held by a member confronting the roller, for example, the cylinder
or at the receiving member side.
(2) (corresponding to FIG. 1 and FIG. 5) In the helical blade type
compressor of (1),
the seal member is freely inserted into an annular groove provided in the
roller outer circumference, and abuts against the annular groove and
cylinder to separate into the pressure in the case and the pressure in the
compression chamber.
According to such constitution, it is easy to adjust the balance of the
thrust load acting in the roller axial direction. Besides, the structure
is simple, the manufacturing efficiency is excellent (processing cost is
lowered, and the assembling performance is improved), so that an
inexpensive compressor may be presented.
(3) (corresponding to FIG. 6, FIG. 7, and FIG. 8) In the helical blade type
compressor of (2),
the annular groove and the seal ring member to be inserted in the annular
groove are provided in a plurality each. According to such constitution,
when using plural seal ring members, by sharing and processing common seal
rings, the cost is reduced.
Preferably, the plural annular rings and seal ring members should be of
same dimensions and materials, individually.
Or, between the plural annular rings and seal ring members, the dimensions
or materials may be different at least at one position.
By using plural seal ring members, it is very effective for keeping the
sealing performance depending on the condition of temperature or pressure.
In such a case, the shape, dimension or material should be selected
depending on the condition of the position of the disposition of each seal
ring member, so that the performance and reliability may be further
enhanced.
(4) (corresponding to FIG. 6) In the helical blade type compressor of (2),
the roller has a flange of a large diameter, and the seal ring is held by
the flange.
By holding the seal ring by the flange, the bending moment is prevented
from acting on the section of the seal ring. As a result, if the seal ring
is thin and made of a soft material, that is, if the rigidity is weak, a
large pressure difference can be sealed by the seal ring member. Hence, a
compact and inexpensive seal structure can be presented.
(5) (corresponding to FIG. 7) In the helical blade type compressor of (2),
the roller is composed of a main body and a lid which can be divided in the
portion of the annular groove.
According to such constitution, the seal ring can be easily fitted in the
annular groove.
In one aspect, a packing is placed between the roller main body and lid,
and they are fixed by a bolt. In such constitution, the sealing
performance of the divided portion is enhanced.
In other aspect, the roller main body and lid are made of same material,
and the surface is treated by nitriding, Ni--P--B plating or other surface
treatment depending on the material of the seal ring member. In such
constitution, the coefficient of thermal expansion of the main body and
lid is the same, and therefore if temperature rise occurs during
operation, distortion hardly occurs. Moreover, by surface treatment
depending on the material of the seal ring, the sliding performance and
reliability are enhanced.
In a different aspect, of the main body and lid, the material of the side
sliding with the seal ring member and the material of the side not sliding
with the seal ring member are different. In such constitution, only the
material of the side sliding with the seal ring member may be made of a
material excellent in sliding performance with the seal ring member.
(6) (corresponding to FIG. 8) In the helical blade type compressor of (2),
the inside diameter of the cylinder inner circumference of the portion
contacting with the seal ring member is different from the inside diameter
of the portion in which the helical blade of the cylinder is disposed.
According to such constitution, the thrust load acting on the roller by the
seal ring member can be set depending on the magnitude of the thrust load
acting on the roller by the helical blade (in the reverse direction of the
thrust load by the seal ring member). Therefore, one thrust load can be
set larger than the other thrust load, so that the roller can be pressed
in one direction so as to be stabilized in motion. As a result, the
vibration and noise can be decreased.
In one aspect, the inside diameter of the cylinder inner circumference of
the portion contacting with the seal ring member is larger than the inside
diameter of the portion in which the helical blade of the cylinder is
disposed.
In other aspect, the inside diameter of the cylinder inner circumference of
the portion contacting with the seal ring member is smaller than the
inside diameter of the portion in which the helical blade of the cylinder
is disposed.
According to such constitution, an adequate thrust load is obtained
depending on whether the pressure in the case is low or high.
(7) (corresponding to FIG. 9, FIG. 10, and FIG. 11) In the helical blade
type compressor of (2),
the annular ring and the seal ring member to be inserted in the annular
ring are provided in a plurality each, and an intermediate pressure
lead-in path for leading in a compression intermediate pressure from the
compression chamber is provided in at least one position of the spaces
divided by the plural seal ring members.
According to such constitution, by leading the intermediate pressure into
the space partitioned by the seal ring members, the pressure difference
acting on each seal ring member may be stably controlled. Accordingly, the
sealing performance is stabilized, and the reliability is also enhanced.
In one aspect (corresponding to FIG. 9), the intermediate pressure lead-in
path is provided at the roller side.
In other aspect (corresponding to FIG. 10), the intermediate pressure
lead-in path is provided at the cylinder side.
In a different aspect (corresponding to FIG. 11), the intermediate pressure
lead-in path is provided at the cylinder and roller sides.
In such constitution, the intermediate pressure can be led in more
securely.
(8) (corresponding to FIG. 12) In the helical blade type compressor of (1),
the seal member is freely inserted into an annular groove provided in the
cylinder inner circumference, and abuts against the annular groove and
roller to separate into the pressure in the case and the pressure in the
compression chamber.
Contrary to the structure in (2), the seal ring member can be provided at
the cylinder side, and similar actions and effects are obtained in such
constitution.
(9) (corresponding to FIG. 13) In the helical blade type compressor of (8),
the cylinder is composed of at least two or more members that can be
divided in the portion of the annular groove.
According to such constitution, the seal ring member may be easily fitted
in the annular groove. In particular, the seal ring member not having
divided portion or the sealing member made of hard material may be fitted
easily.
In one aspect (corresponding to FIG. 13), the two or more members are fixed
by bolts by inserting a packing between them. in such constitution, the
sealing performance of the divided portion is enhanced.
In other aspect (corresponding to FIG. 13), the two or more members are
made of same material, and the surface is treated by nitriding, Ni--P--B
plating or other surface treatment depending on the material of the seal
ring member. In such constitution, the coefficient of thermal expansion of
the members is the same, and therefore if temperature rise occurs during
operation, distortion hardly occurs. Moreover, by surface treatment
depending on the material of the seal ring, the sliding performance and
reliability are enhanced.
In a different aspect (corresponding to FIG. 13), of the two or more
members, the material of the side sliding with the seal ring member and
the material of the side not sliding with the seal ring member are
different. In such constitution, only the material of the side sliding
with the seal ring member may be made of a material excellent in sliding
performance with the seal ring member.
(10) (corresponding to FIG. 14, FIG. 15 and FIG. 16) In the helical blade
type compressor of (8),
the annular groove in which the seal ring member is fitted is divided by a
receiving member holding one end of the cylinder and the end of the
roller, and the seal ring member abuts against the receiving member and
the roller to separate into the pressure in the case and the pressure in
the compression chamber.
According to such constitution, the seal ring member may be fitted easily,
and the structure is simplified.
(11) (corresponding to FIG. 15) In the helical blade type compressor of
(1),
the seal member is inserted into the annular groove provided at the end of
the roller, and cooperates with a receiving member for holding the end of
the roller to separate into the pressure in the case and the pressure in
the compression chamber.
According to such constitution, the seal member may be fitted easily, and
in particular the seal ring member can be installed without disassembling
the roller or cylinder.
In one aspect (corresponding to FIG. 16), the annular groove is opened to
the outer circumferential side of the roller.
In other aspect (corresponding to FIG. 17), the annular groove is opened to
the inside of the roller.
In such constitution, the annular groove can be processed easily, and a
sufficient sealing performance is obtained.
(12) (corresponding to FIG. 18) In the helical blade type compressor of
(1),
the seal member is inserted in the annular groove provided in a receiving
member for holding the end face of the roller, and cooperates with the end
face of the roller to separate into the pressure in the case and the
pressure in the compression chamber.
According to such constitution, the seal member may be fitted easily, and
in particular the seal ring member can be installed without disassembling
the roller or cylinder.
(13) (corresponding to FIG. 19) In the helical blade type compressor of
(11),
an intermediate pressure lead-in path is provided for leading in a
compression intermediate pressure into the seal member from the
compression chamber.
According to such constitution, as an intermediate pressure gas smaller
than the discharge pressure acts at the back side of the seal member, the
gas load acting on the seal ring is decreased, so that the reliability of
the apparatus is enhanced.
(14) (corresponding to FIG. 20) In the helical blade type compressor of
(11),
the annular ring and the seal ring member to be inserted in the annular
ring are provided in a plurality each, and an intermediate pressure
lead-in path for leading in a compression intermediate pressure from the
compression chamber is provided in at least one position of the spaces
divided by the plural seal ring members.
According to such constitution, the pressure difference acting on each seal
member may be stably controlled, and the sealing performance and the
reliability are also enhanced.
(15) (corresponding to FIG. 21) In the helical blade type compressor of
(12),
an intermediate pressure lead-in path is provided for leading in a
compression intermediate pressure into the seal member from the
compression chamber.
According to such constitution, as an intermediate pressure gas smaller
than the discharge pressure acts at the back side of the seal member, the
gas load acting on the seal ring is decreased, so that the reliability of
the apparatus is enhanced.
(16) (corresponding to FIG. 22) In the helical blade type compressor of
(12),
the annular ring and the seal ring member to be inserted in the annular
ring are provided in a plurality each, and an intermediate pressure
lead-in path for leading in a compression intermediate pressure from the
compression chamber is provided in at least one position of the spaces
divided by the plural seal ring members.
According to such constitution, the pressure difference acting on each seal
member may be stably controlled, and the sealing performance and the
reliability are also enhanced.
(17) (corresponding to FIG. 23) In the helical blade type compressor of
(1),
the seal member includes a first seal ring member and a second seal ring
member, the first seal ring member is freely inserted into the annular
groove provided in the roller outer circumference, and abuts against the
annular groove and cylinder to separate into the high pressure side and
low pressure side, and the second seal ring member is inserted in the
annular groove provided at the end face of the roller, and cooperates with
a receiving member for holding the end face of the roller to separate the
high pressure and low pressure.
According to such constitution, sealing is more reliable, and the thrust
load can be adjusted appropriately.
In an aspect (corresponding to FIG. 23), the annular groove for fitting the
second seal ring member is opened also to the roller outer circumferential
side.
(18) (corresponding to FIG. 24) In the helical blade type compressor of
(1),
the seal member has a divided portion in one position along the
circumferential direction, and is formed so as to be expanded in diameter.
According to such constitution, mounting is easy by expanding the diameter
of the seal ring diameter.
In one aspect (corresponding to FIG. 25A), the divided portion of the seal
ring member has six joint faces crossing orthogonally to each other. In
such constitution, at least three joint faces are always in contact, and
if there is a slight gap in other three joint faces, the high pressure and
low pressure can be always separated and sealed. If the seal member is
made of resin and the cylinder is metallic, that is, if the coefficient of
thermal expansion is different, the dimensions can be adjusted by other
three faces.
In other aspect (corresponding to FIG. 25B), the divided portion of the
seal ring member has joint faces provided parallel to the thickness
direction of the seal ring and inclined by a specified angle.
In a different aspect (corresponding to FIG. 25C), the divided portion of
the seal ring member has three joint faces provided parallel to the
thickness direction of the seal ring member.
In other different aspect (corresponding to FIG. 25D), the divided portion
of the seal ring member has three joint faces provided parallel to the
diametral direction of the seal ring member.
In a further different aspect (corresponding to FIG. 25E), the divided
portion of the seal ring member has joint faces provided parallel to the
diametral direction of the seal ring and inclined by a specified angle.
According to such constitution, the sealing performance is assured by a
simple joint structure.
(19) (corresponding to FIG. 24, and FIGS. 25A to 25E) In the helical blade
type compressor of (18),
the divided portion has joint faces, and at least one of the joint faces is
always positioned in the groove for the ring, along with revolution of the
roller, if the seal ring member projects to the maximum extent from the
groove for holding the seal ring.
According to such constitution, secure sealing is assured because at least
one joint face is positioned in the groove for the ring.
(20) (corresponding to FIG. 26 and FIG. 27) In the helical blade type
compressor of (1),
the seal member has a seal ring member and a spring member for thrusting
the seal ring member in the outer circumferential direction.
According to such constitution, since the seal ring member is pressed to
the inner circumference of the cylinder by the thrusting force of the
spring, stable sealing is realized.
In one aspect (corresponding to FIG. 28), the spring member is held by a
guide groove formed in the inner circumference of the seal ring member.
In such constitution, the thrusting force of the spring member acts in good
balance on the seal ring member.
In other aspect (corresponding to FIGS. 50A and 50B), the outside diameter
of the seal ring member in the state before mounting is larger than the
inside diameter of the member which contacts with its outer circumference.
In such constitution, since the outer surface of the seal ring member is
elastically pressed against the member (cylinder) contacting with its
outer circumference, so that the same effect as action of spring member is
obtained.
(21) (corresponding to FIG. 29 and FIG. 31) In the helical blade type
compressor of (1),
the seal member is a seal ring member not having divided portion, and the
seal ring member comprises a ring-shaped main body, a ring side annular
groove provided on the outer circumference of the main body, and a
sub-seal ring member fitted in the ring side annular groove.
According to such constitution, seal leak of the outer circumference of the
seal ring can be effectively prevented by the sub-seal ring member.
(22) (corresponding to FIG. 30 and FIG. 32) In the helical blade type
compressor of (1),
the seal member is a seal ring member not having divided portion, and the
seal ring member comprises a ring-shaped main body, a ring side annular
groove provided on the inner circumference of the main body, and a
sub-seal ring member fitted in the ring side annular groove.
According to such constitution, seal leak of the inner circumference of the
seal ring can be effectively prevented by the sub-seal ring member.
(23) (corresponding to FIG. 33) In the helical blade type compressor of
(1),
the seal member is a seal ring member not having divided portion, and the
seal ring member has a ring side annular groove opened at its outer
circumferential side, and the section of the ring side annular groove is
U-form or V-form, and the opening side is at high pressure.
(24) (corresponding to FIG. 33) In the helical blade type compressor of
(1),
the seal member is a seal ring member not having divided portion, and the
seal ring member has a ring side annular groove opened at its inner
circumferential side, and the section of the ring side annular groove is
U-form or V-form, and the opening side is at low pressure.
In one aspect (corresponding to FIG. 33 and FIG. 43), a spring member is
inserted in the ring side annular groove. In such constitution, an initial
sealing force is obtained by the spring member, and therefore the sealing
performance is stabilized.
In other aspect (corresponding to FIG. 34 and FIG. 35), a groove for
sub-seal ring is formed in a member contacting with the seal ring, and a
sub-seal ring member is fitted in the groove for sub-seal ring.
(25) (corresponding to FIG. 1, FIG. 2, FIG. 36, and FIG. 37) In the helical
blade type compressor of (1),
the seal member is a seal ring member having an outer circumference, an
inner circumference, and a plane enclosing them, and the plane is composed
so that the area sliding with the member contacting with the seal ring is
smaller than the area not sliding.
According to such constitution, the surface pressure acting on the plane of
the seal ring can be adjusted. By the adjustment, the sealing performance
and reliability may be optimally controlled.
In an aspect (corresponding to FIG. 36 and FIG. 37), a clearance opened at
the low pressure side is provided on the plane.
In this constitution, the surface pressure acting on the plane can be
adjusted by the clearance. On the opposite side of the opening side of
this clearance, a high pressure is acting on the whole, but since the
clearance opened at the low pressure side is provided, when the surface
pressure of the sliding surface rises, the force acting on the seal ring
main body is raised at the same time.
If the pressing force is insufficient, by employing this structure, the
sealing performance may be enhanced easily.
In other aspect (corresponding to FIG. 38), a clearance opened at the high
pressure side is provided on the plane. In this constitution, when the
surface pressure of the sliding surface drops, the force acting on the
seal ring main body is lowered at the same time.
(26) (corresponding to FIG. 39) In the helical blade type compressor of
(12),
the seal member inserted in the annular groove at the end face of the
roller is a seal ring member having seal member side annular grooves at
the outer circumference and inner circumference, sub-seal ring members are
inserted in these seal member side annular grooves, and it also has an
intermediate pressure lead-in path for leading the compression
intermediate pressure in the compression chamber to the opposite side of
the sliding side of the seal ring.
(27) (corresponding to FIG. 40) In the helical blade type compressor of
(26),
a spring member is provided at an opposite side of the sliding surface of
the seal ring.
According to such constitution, an initial sealing pressure can be obtained
by the spring member, so that a stable sealing performance is assured even
right after starting up.
In one aspect (corresponding to FIG. 41), a clearance not communicating
with the inner and outer circumferential sides of the seal ring is formed
on the sliding surface of the seal ring member, and moreover an
intermediate pressure lead-in path for leading a compression intermediate
pressure to the clearance is provided in the seal ring. In such
constitution, since the intermediate pressure can be guided into the
clearance confronting the sliding surface, the surface pressure on the
sliding surface drops, and the force acting on the seal ring main body may
be lowered at the same time.
In other aspect (corresponding to FIG. 42), the plural seal ring members
are composed of ring-shaped main body, ring side annular groove disposed
at the inner circumference of the main body, and sub-seal ring member
fitted in the ring side annular groove.
In such constitution, seal leak of the seal ring inner circumference can be
effectively prevented by the sub-seal ring member.
In a different aspect (corresponding to FIG. 43), the plural seal ring
members have a ring side annular groove opened at the outer
circumferential side thereof, and the section of the ring side annular
groove is either U-form or V-form, and the pressure is higher at the
opening side.
(28) (corresponding to FIG. 1 and FIG. 2) In the helical blade type
compressor of (1),
the material of the seal member is engineering plastic (resin).
According to such constitution, by using the engineering plastic material,
it is easier to form and process, the elasticity and a certain rigidity
are maintained, so that the seal structure excellent in mounting, sealing,
sliding and reliability is presented.
In one aspect (corresponding to FIG. 1 and FIG. 2), the principal component
of the material of the seal member made of engineering plastic is PEEK
(polyether ether ketone). In such constitution, since the rigidity is
high, heat resistance is excellent and coefficient of friction is low, it
is suited to the case in which the load applied to the seal ring is large,
and the reliability and sealing performance are enhanced. It is also
possible to process by injection forming, and the manufacturing
performance is superior.
In other aspect (corresponding to FIG. 1 and FIG. 2), the principal
component of the material of the seal member made of engineering plastic
is fluoroplastic composed of PEEK or PFA. In such constitution, the
material is relatively soft, and it is effective to fit to the shape
smoothly.
In a different aspect (corresponding to FIG. 1 and FIG. 2), the principal
component of the material of the seal member made of engineering plastic
is PI (polyimide).
In other different aspect (corresponding to FIG. 1 and FIG. 2), the
principal component of the material of the seal member made of engineering
plastic is PPS (polyphenylene sulfide).
According to such constitution, the seal member can be composed of a
relatively inexpensive material.
(29) (corresponding to FIG. 44) In the helical blade type compressor of
(1),
the seal member is a seal ring member, and the inner end portion of the
seal ring member to be inserted into the cylinder is chamfered.
According to such constitution, owing to the chamfering, after inserting
the seal ring member, when inserting together with the roller into the
cylinder, the chamfering acts as the guide of the outer circumference of
the seal ring. Hence, the assembling performance is notably improved.
(30) (corresponding to FIG. 45) In the helical blade type compressor of
(1),
the seal member is a seal ring member, and the outer end portion of the
seal ring member to be inserted into the cylinder is chamfered.
In this constitution, the same effect as in (29) is obtained.
(31) (corresponding to FIG. 51) A refrigeration cycle apparatus using the
helical blade type compressor of (1), in which the refrigerant used in the
refrigeration cycle is a refrigerant higher in condensation or evaporation
pressure than R22.
When using a refrigerant high in condensation or evaporation pressure, the
absolute pressure difference between the high pressure side and low
pressure side of the cycle is higher. In such condition, the sealing
performance of high and low pressure in the cylinder tends to be inferior,
and the thrust load acting on the roller is larger. However, by using the
seal member in the invention, the sealing performance is improved, and the
thrust load can be adjusted, and it is particularly effective when using
such refrigerant.
In one aspect, the refrigerant used in the refrigeration cycle is R32 or an
HFC system refrigerant containing R32. That is, if using an HFC system
refrigerant which is a substitute CFC, the same effect as in (72) is
obtained.
In other aspect, the HFC system refrigerant used in the refrigeration cycle
is a mixed refrigerant composed of R410A or R407C. By using an HFC system
mixed refrigerant, the same effect as in (72) is obtained, and in
particular, as compared with R22, R410A is higher in condensation pressure
or evaporation pressure by about 1.5 times. The use of the seal ring in
such condition is particularly effective means for enhancement of
performance and reliability.
Additional objects and advantages of the invention will be set forth in the
description which follows, and in part will be obvious from the
description, or may be learned by practice of the invention. The objects
and advantages of the invention may be realized and obtained by means of
the instrumentalities and combinations particularly pointed out
hereinafter.
BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWING
The accompanying drawings, which are incorporated in and constitute a part
of the specification, illustrate presently preferred embodiments of the
invention, and together with the general description given above and the
detailed description of the preferred embodiments given below, serve to
explain the principles of the invention.
FIG. 1 is a longitudinal sectional view showing a first embodiment of the
invention;
FIG. 2 is a longitudinal sectional view showing only the compression
mechanism of the same;
FIG. 3 is a cross sectional view along line III--III in FIG. 2;
FIG. 4 is a cross sectional view along line IV--IV in FIG. 2;
FIG. 5 is.a longitudinal sectional view showing a second embodiment;
FIG. 6 is a longitudinal sectional view showing a third embodiment;
FIG. 7 is a longitudinal sectional view showing a modified example of the
third embodiment;
FIG. 8 is a longitudinal sectional view showing a modified example of the
third embodiment;
FIG. 9 is a longitudinal sectional view showing a fourth embodiment;
FIG. 10 is a longitudinal sectional view showing a modified example of the
fourth embodiment;
FIG. 11 is a longitudinal sectional view showing a modified example of the
fourth embodiment;
FIG. 12 is a longitudinal sectional view showing a fifth embodiment;
FIG. 13 is a longitudinal sectional view showing a modified example of the
fifth embodiment;
FIG. 14 is a longitudinal sectional view showing a modified example of the
fifth embodiment;
FIG. 15 is a longitudinal sectional view showing a sixth embodiment;
FIG. 16 is a longitudinal sectional view showing a modified example of the
sixth embodiment;
FIG. 17 is a longitudinal sectional view showing a modified example of the
sixth embodiment;
FIG. 18 is a longitudinal sectional view showing a modified example of the
sixth embodiment;
FIG. 19 is a longitudinal sectional view showing a seventh embodiment;
FIG. 20 is a longitudinal sectional view showing a modified example of the
seventh embodiment;
FIG. 21 is a longitudinal sectional view showing a modified example of the
seventh embodiment;
FIG. 22 is a longitudinal sectional view showing a modified example of the
seventh embodiment;
FIG. 23 is a longitudinal sectional view showing an eighth embodiment;
FIG. 24 is a perspective view showing a ninth embodiment;
FIGS. 25A to 25E are perspective views showing the junction of the seal
ring for explaining the ninth embodiment;
FIG. 26 is a perspective view showing a tenth embodiment;
FIG. 27 is a longitudinal sectional view showing essential parts for
explaining the tenth embodiment;
FIG. 28 is a longitudinal sectional view showing a modified example of
essential parts of the tenth embodiment;
FIG. 29 is a perspective view showing s seal ring in an eleventh
embodiment;
FIG. 30 is a perspective view showing s seal ring in the eleventh
embodiment;
FIG. 31 is a longitudinal sectional view showing a mounting example of the
eleventh embodiment;
FIG. 32 is a longitudinal sectional view showing a mounting example of the
eleventh embodiment;
FIG. 33 is a longitudinal sectional view showing a mounting example of the
eleventh embodiment;
FIG. 34 is a longitudinal sectional view showing a twelfth embodiment;
FIG. 35 is a longitudinal sectional view showing a modified example of the
twelfth embodiment;
FIG. 36 is a longitudinal sectional view showing a modified example of the
twelfth embodiment;
FIG. 37 is a longitudinal sectional view showing a modified example of the
twelfth embodiment;
FIG. 38 is a longitudinal sectional view showing a modified example of the
twelfth embodiment;
FIG. 39 is a longitudinal sectional view showing a thirteenth embodiment;
FIG. 40 is a longitudinal sectional view showing a modified example of the
thirteenth embodiment;
FIG. 41 is a longitudinal sectional view showing a modified example of the
thirteenth embodiment;
FIG. 42 is a longitudinal sectional view showing a modified example of the
thirteenth embodiment;
FIG. 43 is a longitudinal sectional view showing a modified example of the
thirteenth embodiment;
FIG. 44 is a longitudinal sectional view showing a fourteenth embodiment;
FIG. 45 is a longitudinal sectional view showing a modified example of the
fourteenth embodiment;
FIG. 46 is a longitudinal sectional view showing a modified example of the
fourteenth embodiment;
FIG. 47 is a longitudinal sectional view showing a modified example of the
fourteenth embodiment;
FIG. 48 is a longitudinal sectional view showing a modified example of the
fourteenth embodiment;
FIGS. 49A and 49B are longitudinal sectional view and plan view showing the
assembling process of the compression mechanism for explaining the
fourteenth embodiment;
FIGS. 50A and 50B are front view and plan view showing the assembling jig
of the compression mechanism for explaining the fourteenth embodiment; and
FIG. 51 is a structural diagram of a refrigeration cycle apparatus showing
a fifteenth embodiment.
DETAILED DESCRIPTION OF THE INVENTION
Referring now to the drawings, embodiments of the invention are described
in detail below.
(First embodiment)
FIG. 1 is a longitudinal sectional view showing a helical blade type
compressor (hereinafter called compressor) of a first embodiment.
This compressor comprises an enclosed case (hereinafter called case) 1, a
motor 2 disposed in the upper part in the case 1, and a compression
mechanism 3 disposed in the lower part in the case 1 and driven by the
motor 2.
The compressor in this embodiment is designed to suck a low pressure gas
into the case 1 through a suction pipe shown in FIG. 4, compress in the
compression mechanism 3, and discharge out of the case 1 through a
discharge pipe shown in FIG. 5. Such compressor is generally called a
"case internal low pressure type".
The motor 2 consists of a stator 7 fixed in the inner side of the case 1,
and a rotor 8 which rotates in the stator 7. From the rotor 8, a
crankshaft 9 having a crank 9a at the lower end side is projecting toward
the compression mechanism 3 side.
On the other hand, the compression mechanism 3 has a main bearing member 10
and a subsidiary bearing member 11 for rotatably holding the crankshaft 9.
Between the main bearing member 10 and subsidiary bearing member 11, a
cylindrical cylinder 12 is held. The cylinder 12 has its upper end opening
and lower end opening abutting against the lower surface of the main
bearing member 10 and the upper surface of the subsidiary bearing member
11, respectively, and is held with its central axis coinciding with the
center line of the crankshaft 9.
In the cylinder 12, further, a circular columnar roller 14 is held by the
crank 9a of the crankshaft 9. Therefore, the roller 14 rotates
eccentrically in the cylinder 12 as the crankshaft 9 is driven. At the
maximum eccentric portion, as show in the diagram, part of the outer
circumference contacts with the inner circumference of the cylinder 12.
Between the roller 14 and the subsidiary bearing member 11, an Oldham
mechanism 15 for defining the rotation of the roller 14 is interposed. By
the Oldham mechanism, the rotor 14 revolves about the axial line of the
crankshaft 9 without rotating.
On the outer circumference of the roller 14, moreover, helical grooves 16
of uneven pitches are formed so that the pitch may be gradually narrower
from top to bottom. In the helical grooves 16, helical blades 17 formed
similarly in uneven pitches are fitted. Since the helical blade 17 is
composed in such dimension that its outer surface may always abut
elastically against the inner circumference of the cylinder 12, when the
roller 14 rotates eccentrically in the cylinder 12, it projects from
within the helical groove 16.
According to such constitution, at the outer side of the roller 14, a
compression chamber 18 of a crescent cross section is formed by the inner
circumference of the cylinder 12 and the helical blade 17. This
compression chamber 18 moves helically from top to bottom while rotating
in the peripheral direction when the roller 14 is driven eccentrically.
The volume of the compression chamber 18 corresponds to the pitch of the
helical blade 17, and becomes gradually smaller as moving downward. As a
result, the gas contained in the compression chamber 18 is compressed.
At the lower end of the roller 14, a seal ring 19 is provided to partition
the cylinder 12 into the high pressure side and low pressure side. The
seal ring 19 is freely fitted in a groove 20 for seal ring provided in the
roller 14 so as to abut always against the inner circumference of the
cylinder regardless of eccentric rotation of the roller 14. According to
such constitution, the highest pressure is achieved in the compression
chamber 18a divided by the lower end portion of the helical blade 17 and
the upper side of the seal ring 19.
Since this compressor is of case internal low pressure type, a suction port
21 for leading in the low pressure gas in the case 1 into the compression
chamber 18 is provided at the upper end side of the roller 14. The low
pressure gas in the case 1 is designed to be sucked into the suction port
21 through a low pressure gas path 22 provided in the crankshaft 9. At the
lower end side of the cylinder 12, a discharge pipe 5 is provided in order
to take out a high pressure gas from within the compression chamber 18a at
the lowest end divided by the helical blade 17 and seal ring 19.
According to such seal ring structure, as explained below, the low pressure
side and high pressure side can be sealed securely while adjusting the
thrust load acting on the main bearing member 10 or subsidiary bearing
member 11 from the roller 14. This effect is specifically described below
while referring to FIG. 2.
FIG. 2 schematically describes the pressure state acting on the roller 14.
As shown in the diagram, the compression chamber 18a achieving the highest
pressure is divided by the helical blade 17 and seal ring 19. The pressure
in the compression chamber 18a acts on the lower surface of the helical
blade 17 and the upper wall of the helical groove 16, and generates an
upward thrust load F1 on the roller 14. On the other hand, the pressure in
the same compression chamber 18a acts on the upper surface of the seal
ring 19 and the lower wall of the groove 20 for seal ring, and generates a
downward thrust load F2 on the roller 14.
Other compression chambers 18 than the compression chamber 18a achieving
the highest pressure are partitioned by helical blades 17, and therefore
the upward and downward thrust loads are canceled in each compression
chamber 18. Hence, as the thrust load acting on the roller 14, it is
enough only to consider the balance of thrust loads F1 and F2 generated in
the compression chamber 18a achieving the highest pressure.
In the compression chamber 18a, when the pressure acting area at the
helical blade 17 side and the pressure acting area at the seal ring 19
side are equal, the upward thrust load F1 and downward thrust load F2 are
balanced, and the resultant force of the thrust load acting on the main
bearing member 10 or subsidiary bearing member 11 may be regarded to be
nearly 0.
Suppose the suction gas pressure, that is, the pressure of low pressure gas
filling the case 1 to be Ps, and the discharge gas pressure, that is, the
pressure of high pressure gas in the compression chamber 18a to be Pd. In
this case, a differential pressure .DELTA.P=Pd-Ps acts downward on the
upper surface of the seal ring 19 and the bottom wall of the groove 20 for
ring, and the same pressure .DELTA.P acts also on the lower surface of the
helical blade 17 and the upper wall of the helical groove 16.
The value obtained by integrating this differential pressure and he
pressure acting area is equal to the thrust load F1 or F2.
First, the pressure acting area A1 and the thrust load F1 at the helical
blade 17 side are discussed.
FIG. 3 is a cross sectional view showing an arrow view of III--III in FIG.
2.
Supposing the inside diameter of the cylinder 12 to be Da and the outside
diameter of the helical groove 16 to be Db, the pressure acting area A1 is
A1=(Da.sup.2 -Db.sup.2).pi./4
and the thrust load F1 is
i F1=.DELTA.P.multidot.A1=.DELTA.P(Da.sup.2 -Db.sup.2).pi./4.
Next are discussed the pressure acting area A2 and the thrust load F2 at
the seal ring 19 side.
FIG. 4 is a cross sectional view showing an arrow view of IV--IV in FIG. 2.
Supposing the outside diameter of the seal ring 19 to be Dc and the outside
diameter of the groove 20 for seal ring to be Dd, the pressure acting area
A2 is
A2=(Da.sup.2 -Db.sup.2).pi./4
and the thrust load F2 is
F2=.DELTA.P.multidot.A2=.DELTA.P(Da.sup.2 -Db.sup.2).pi./4.
In this first embodiment, the outside diameter Dc of the seal ring 19 is
designed to be equal to the inside diameter Da of the cylinder 12, and
that the outside diameter Dd of the groove 20 for seal ring equal to the
outside diameter Db of the helical groove 16. Hence, F1=F2, so that the
thrust load acting on the roller 14 may be 0.
As clear herein, by properly designing the outside diameter of the seal
ring 19 and the dimension of the groove 20 for ring, it is easy to define
F1>F2 or F1<F2, and the allowance for adjustment of thrust load is wide.
That is, according to this seal ring structure, the low pressure side (the
pressure in the case) and the high pressure side (the pressure in the
compression chamber) can be sealed securely, and the thrust load between
the main bearing member 10 and subsidiary bearing member 11 can be
adjusted easily. Therefore, without causing excessive load on the roller
14, it is possible to seal securely.
As the material for the seal ring 19, a proper material may be used, and in
particular, an engineering plastic material (resin material) is preferred.
By the use of engineering plastic material, it is possible to form or
process the seal ring 19 easily, and elongation and a certain rigidity may
be assured, and a seal structure excellent in mounting, sealing, sliding
and reliability may be presented.
In this case, by using PEEK (polyether ether ketone) as the principal
component of the material of the seal ring 19, so that the seal ring 19
high in rigidity, excellent in heat resistance and small in coefficient of
friction is presented. This material is suited to the case in which the
load applied to the seal ring 19 is large, and the reliability and sealing
performance are enhanced. It is also possible to process by injection
forming, and the manufacturing performance is superior.
As the principal component of the seal ring 19 made of engineering plastic,
fluoroplastic composed of PEEK or PFA may be used. These materials are
relatively soft, and it is effective to fit to the shape smoothly.
Besides, the principal component of the seal ring 19 made of engineering
plastic may be PI (polyimide), or PPS (polyphenylene sulfide). By using
such materials, the seal ring 19 can be composed of a relatively
inexpensive material.
(Second embodiment)
FIG. 5 is a schematic structural diagram showing a second embodiment. Same
constituent elements as in the first embodiment are identified with same
reference numerals.
As compared with the first embodiment relating to the helical blade type
compressor of case internal low pressure type, the compressor of this
embodiment is of case internal high pressure type.
That is, in the compressor of this embodiment, a low pressure gas is sucked
directly into the cylinder 12 through a suction pipe 21 shown in the
diagram. The helical blades 17 in this embodiment are formed to be
gradually narrower in pitch from bottom to top, and the low pressure gas
sucked into the cylinder 12 is gradually compressed as moving from bottom
to top together with the compression chamber 18. The compressed high
pressure gas is discharged into the case 1 through a discharge port 22
provided in the main bearing member 10. Besides, at the upper end of the
case 1, a discharge pipe 23 for discharging the high pressure gas to
outside of the case 1 is provided.
In this embodiment, too, the seal ring 19 is attached to the lower end of
the roller 14. However, the compression chamber 18a divided by the seal
ring 19 and the helical blade 17 is a low pressure Ps atmosphere,
different from the first embodiment, while the lower side of the seal ring
19 is a high pressure Pd atmosphere. Therefore, an upward thrust load F2
corresponding to the pressure acting area by the seal ring 19 and the
differential pressure .DELTA.P=Pd-Ps acts on the seal ring 19. By
balancing the thrust load F2 with the downward thrust load F1 acting on
the roller 14 by the helical blade 17, the same effects as in the first
embodiment are obtained.
(Third embodiment)
Referring then to FIG. 6 to FIG. 8, a third embodiment is described.
FIG. 6 shows the compression mechanism 3 in the helical blade type
compressor of case internal low pressure type.
At the lower end of the roller 14 in this embodiment, a roller flange 31 of
a large diameter is formed. A groove 20 for seal ring for holding the seal
ring 17 is formed so that its bottom may be flush with the upper surface
of the roller flange 31, and this surface is a seal ring sliding surface
32.
In such constitution, since the outer circumference of the seal ring 19 can
be held by the upper surface (seal ring sliding surface 32) of the roller
flange 31, bending moment does not act on the section of the seal ring 19.
Therefore, breakage of the seal ring 19 may be effectively prevented, and
the reliability is enhanced.
Moreover, in the constitution shown in FIG. 7, the roller flange 31 is
formed as a roller flange part 31' that can be separated from the roller
14 (main body). The groove 20 for seal ring is formed so as to divide the
roller flange pat 31' by joining with the lower surface of the roller 14.
The roller flange part 31' is fixed by a junction bolt 34 in a state of
inserting a seal member 33 such as packing into the junction of the roller
14.
In this embodiment, the roller 14 (main body) and roller flange part 31'
are made of same material, and the sliding surface 32 with the seal ring
19 is treated by nitriding, Ni--P--B plating or other surface treatment,
depending on the material of the seal ring 19.
In such constitution, the seal ring 19 can be detached or attached easily.
Still more, by using an appropriate material, the coefficient of thermal
expansion is equal between the roller 14 and flange part 31', and if
temperature rise occurs during operation, distortion hardly occurs.
Besides, by surface treatment depending on the material of the seal ring
19, the sliding performance and reliability are enhanced.
Incidentally, if the roller flange part 31' and roller 14 are made of
different materials, at least the material of the roller flange part 31'
may be properly selected, or a proper surface treatment may be applied to
the sliding surface 32.
On the other hand, in the constitution shown in FIG. 8, different from the
constitution shown in FIG. 6, a step 36 is formed at the lower end of the
cylinder 12 so that the inside diameter Da of the cylinder 12 in the
portion sliding with the helical blade 17 and the inside diameter of the
cylinder 12 in the portion sliding with the seal ring 19 (=seal ring
outside diameter Dc) may be in the relation of Dc>Da.
According to such constitution, the thrust load acting on the roller 14 by
the seal ring 19 can be set depending on the magnitude of the thrust load
acting on the roller 14 by the helical blade 17 (in reverse direction of
the thrust load by the seal ring 19). As a result, the former thrust load
can be set larger than the latter thrust load, and the roller 14 can be
pressed to the subsidiary bearing member 11 side, so that the motion can
be stabilized. Hence, the vibration and noise can be decreased.
In the case of the case internal high pressure type, contrary to this
embodiment, it may be set in the relation of Dc<Da.
(Fourth embodiment)
Referring next to FIG. 9, FIG. 10 and FIG. 11, a fourth embodiment is
described below.
This fourth embodiment relates to a constitution in which a plurality of
seal rings are provided, and in the constitution shown in FIG. 9, FIG. 10
and FIG. 11, first and second seal rings 19a, 19b are fitted respectively
into grooves 20a, 20b for first and second seal rings provided in the
roller 14.
In the constitution shown in FIG. 9, in the space divided by the first and
second seal rings 19a, 19b, an intermediate pressure lead-in path 41 for
leading in the compressed intermediate pressure from the compression
chamber 18 is provided.
In the constitution shown in FIG. 10, an intermediate pressure lead-in path
41' is provided at the cylinder 12 side, while the constitution shown in
FIG. 11 has the two kinds of the intermediate pressure lead-in paths 41,
41'.
According to such constitutions, by leading the compressed intermediate
pressure into the space partitioned by the first and second seal rings
19a, 19b, the pressure acting on the seal rings 19a, 19b may be controlled
stably, and hence the sealing performance is stabilized and the
reliability is enhanced.
(Fifth embodiment)
A fifth embodiment is described below while referring to FIG. 12 to FIG.
14.
This embodiment, as shown in FIG. 12, relates to a constitution of forming
a groove 51 for seal ring for holding the seal ring 19 at the cylinder 12
side.
Also in such constitution, the same effects as in the first embodiment are
obtained.
In the constitution shown in FIG. 13, the cylinder 12 is divided into upper
and lower sections by the portion of the groove 51 for seal ring, and the
groove 51 for seal ring is divided by mounting a part 42 at the main body
side of the cylinder 12. A packing 53 is inserted in the junction of the
main body of the cylinder 12 and the part 52, and they are fixed by a
mounting bolt 54 shown in the diagram.
In such constitution, the same effects as shown in FIG. 7 are obtained.
In the example shown in FIG. 14, the groove 51 for seal ring is divided by
a annular recess 55 formed at the lower end side of the cylinder 12 and
the upper surface of the subsidiary bearing member 11.
In such constitution, same as shown in FIG. 8, occurrence of bending moment
on the seal ring 19 can be effectively prevented.
(Sixth embodiment)
A sixth embodiment is described below while referring to FIG. 15 to FIG.
18.
This embodiment relates to a constitution in which the seal ring is
provided on the sliding surface of the roller 14 and the subsidiary
bearing member 11.
First, in an example shown in FIG. 15 to FIG. 17, a groove 61 for seal ring
is provided at the lower end of the roller 14, and a seal ring 62 if put
in the groove 61 for seal ring.
In such constitution, too, the high pressure side (pressure in the
compression chamber) and the low pressure side (the pressure in the case)
can be sealed securely.
In the constitution shown in FIG. 16, the groove 61 for seal ring is formed
to be opened to the outer circumferential side of the roller 14. This
constitution is applied to the case internal low pressure type, and the
seal ring 61 is pressed to the roller 14 side for receiving a high
pressure in the compression chamber 18a on the outer circumference.
In the case of the case internal high pressure type, as shown in FIG. 17,
the groove 61 for seal ring is composed to be opened to the inner
circumferential side of the roller 14. In this constitution, the seal ring
61 receives a high pressure in the case 1 is received on the inner
circumference, and is pressed to the roller 14 side.
In an example shown in FIG. 18, a groove 63 for seal ring is provided at
the subsidiary bearing member 11 side, and a seal ring 62 is put in the
groove 63 for seal ring. In this constitution, too, the same effects as
shown in FIG. 15 are obtained.
(Seventh embodiment)
A seventh embodiment is described while referring to FIG. 19 to FIG. 22.
This embodiment, similar to the sixth embodiment, relates to a constitution
of forming a seal ring 62 at the end of the roller 14, in which an
intermediate pressure lead-in path 71 is provided at the side (back side)
other than the sliding surface of the seal ring 62 for leading in a
compressed intermediate pressure from the compression chamber 18 side.
In an example shown in FIG. 19, relating to the constitution in FIG. 15,
the intermediate pressure lead-in path 71 is provided at the roller 14
side, and an example shown in FIG. 21 relates to a constitution shown in
FIG. 18, in which the intermediate pressure lead-in path 71 is provided at
the cylinder 12 and subsidiary bearing member 11 side.
According to such constitution, as the intermediate pressure smaller than
the discharge gas pressure acts on the back side of the seal ring 62, the
gas load acting on the seal ring 62 can be reduced, so that the
reliability of the apparatus is enhanced.
Further, the seal ring 62 may be divided into two seal rings 61a, 61b as
shown in FIG. 20 and FIG. 22, and in this case the intermediate pressure
lead-in path 71 is connected to the space divided by the seal rings 61a,
61b.
In such constitution, the pressure difference acting on the seal rings 61a,
61b can be stably controlled, and the sealing performance and reliability
are enhanced.
(Eighth embodiment)
An eighth embodiment is described below while referring to FIG. 23.
This embodiment includes both the seal ring 19 in the first embodiment
(FIG. 1) and the seal ring 62 in the sixth embodiment (FIG. 15) as the
seal structure.
According to such constitution, effects of both first embodiment and sixth
embodiment are obtained, secure sealing is realized, while adjustment of
thrust load is also easy.
As the constitution of the grooves 20, 61 for seal ring for holding the
seal rings 19, 62, the constitutions mentioned in the first to seventh
embodiments may be appropriately employed. Of course, it can be also
applied to the compressor of case internal high pressure type.
(Ninth embodiment)
A ninth embodiment is described below while referring to FIG. 24 and FIG.
25.
This embodiment relates to a specific constitution of the seal ring 19
(62).
FIG. 24 is a solid view of roller 14 and seal ring 19. Herein, the seal
ring 19 has a junction 91 composed to be separable, in part in the
circumferential direction. Therefore, by expanding the seal ring 19 in the
portion of the junction 91, it can be easily fitted into the groove 20 for
seal ring of the roller 14.
FIGS. 25A to 25E are enlarged views of the structure of the junction 91 of
the seal ring 19.
The junction 91a shown in FIG. 25A has two joint faces 1 to 6, and the
asterisked faces 1, 2, 6 are always contacting during operation of the
compressor and function as the seal means. Other three joint faces have a
specified gap for absorbing difference in thermal expansion between the
seal ring 19 and cylinder 12, and are not always contacting.
According to such constitution, while effectively absorbing dimensional
difference due to thermal expansion between members, it is effective to
seal securely.
The junction 91b shown in FIG. 25B has a joint face 1 provided along the
thickness direction of the seal ring 19, and the joint face 1 is inclined
by a specified angle .theta. to the diametral direction of the seal ring
19. According to such constitution, the seal may be formed in a extended
form.
The junction 91c shown in FIG. 25C has three joint faces 1, 2, 3, and these
joint faces 1, 2, 3 are formed along the thickness direction of the seal
ring 19, that is, disposed in a key shape. In such constitution, the
asterisked joint face 1 is always contacting during operation, and acts to
keep sealing performance.
The junction 91d shown in FIG. 25D has three joint faces 1, 2, 3, and these
joint faces 1, 2, 3 are formed parallel to the diametral direction of the
seal ring 19, that is, disposed in a key shape. In such constitution, the
asterisked joint face 2 among joint faces is always contacting during
operation, and acts to keep sealing performance.
The junction 91e shown in FIG. 25E has a joint face provided along the
diametral direction of the seal ring 19, and the joint face is inclined by
a specified angle .theta. to the thickness direction of the seal ring 19.
According to such constitution, the seal may be formed in a extended form.
(Tenth embodiment)
A tenth embodiment is described below while referring to FIG. 26, FIG. 27,
and FIG. 28.
This embodiment relates to a constitution in which a spring member 101 is
provided inside the seal ring 19 for thrusting the seal ring to the
outside in the diametral direction.
FIG. 26 is a solid perspective view of roller 14, seal ring 19, and spring
member 101. The spring member 101 is formed in a C-form, and is fitted to
the inner circumference of the seal ring 19 while being compressed in the
diametral direction.
The seal ring 19 has the junction 91, and it is fitted into the groove 20
for seal ring while expanding by the junction 91.
FIG. 27 is a longitudinal sectional view showing the configuration of the
seal ring 19, groove 20 for seal ring, and spring member 101.
In such constitution, since the seal ring 19 is pressed against the inner
circumference of the cylinder 12 by the thrusting force of the spring
member 101, a more stable sealing effect is obtained.
In an example shown in FIG. 28, a guide groove 102 is provided in the inner
circumference of the seal ring 19 in order to hold the spring member 101
at the intermediate position in the thickness direction of the seal ring
19.
According to such constitution, the thrusting force of the spring member
101 acts on the seal ring 19 in a favorable balance.
(Eleventh embodiment)
An eleventh embodiment is described below while referring to FIG. 29 to
FIG. 32.
FIG. 29 relates to a seal ring 19 not having divided portion, in which an
annular groove 111 is provided in its outer circumference, and a first
sub-seal ring 112 is fitted in the annular groove 111.
On the other hand, in FIG. 30 relating to a seal ring 19 without divided
portion, an annular groove 113 is provided in its inner circumference, and
a second sub-seal ring 114 is fitted in the annular groove 113.
FIG. 31 and FIG. 32 show the state of installation of thus constituted seal
ring 19 in the groove for seal ring, 20, 61, formed in the roller 114.
According to such constitution, since divided portion is not provided in
the seal ring 19, seal leak can be prevented effectively. Moreover, the
sealing performance is enhanced by the sub-seal rings 112, 114.
In the constitution shown in FIG. 33, the annular groove 111 is formed in a
section of U-form or V-form, and a spring member 115 is inserted in the
annular groove.
In this embodiment, by properly selecting the opening direction of the
annular grooves 111, 113 depending on the case internal high pressure type
or case internal low pressure type, the pressure acting on the seal ring
19 can be adjusted.
(Twelfth embodiment)
Referring now to FIG. 34 to FIG. 38, a twelfth embodiment is described.
In this embodiment, the sub-seal rings 112, 113 are not provided at the
seal ring 19 side, but are provided at the roller 14 or cylinder 12 side
contacting with the seal ring 19.
FIG. 34 shows an example in which a sub-seal ring 112 is held in a holding
groove 121 opened at the cylinder 12 side, and FIG. 35 is an example in
which a sub-seal ring 114 is held in a holding groove 122 opened at the
roller 14 side.
In such constitution, the same effects as in the eleventh embodiment are
obtained. In this example, preferably, it should be constituted depending
on the case internal low pressure and high pressure types so that the
pressure may be high at the opposite side of the side of the disposition
of the sub-seal rings 112, 114.
In FIG. 36 to FIG. 38, relating to the constitution shown in FIG. 34,
clearances 124a to 124c are formed in the sliding surfaces of the seal
ring 19 and the upper surface of the roller flange 31 in order to adjust
the sliding surface area.
In such constitution, the surface pressure acting on the sliding surface of
the seal ring 19 can be adjusted, and the sealing performance and the
reliability may be optimally controlled.
(Thirteenth embodiment)
A thirteenth embodiment is described by reference to FIG. 39 to FIG. 43.
This embodiment is similar to the constitution of the seventh embodiment
(FIG. 19), except that seal rings 112, 114 as explained in the eleventh
embodiment are used as the seal ring 62.
That is, as shown in FIG. 39, the seal ring 62 is contained in the groove
61 for seal ring provided at the lower end face of the roller 14. The seal
ring 62 is provided with the sub-seal rings 112, 114, respectively, on the
outer circumference and inner circumference. The intermediate pressure
lead-in path 71 is constituted so as to communicate between the
compression chamber 18 in the intermediate portion in the compression
direction and the groove 61 for seal ring.
According to such constitution, same as in the seventh embodiment, it is
easy to adjust the pressure acting on the seal ring 61, and secure sealing
is realized.
FIG. 40 shows an example of installing a spring member 131 for pressing the
seal ring 61 to the subsidiary bearing member 11, in the groove 61 for
seal ring. In such constitution, an initial pressure can be applied to the
seal ring 62, and a stable sealing performance from right after starting
operation.
In the constitution in FIG. 41, a clearance 132 is provided in the surface
opposite to the sliding surface of the seal ring, and a small hole 133 for
leading an intermediate pressure into the clearance 132 is formed.
According to such constitution, the surface pressure of the sliding surface
can be lowered and the pressure acting on the seal ring 62 can be lowered.
In the constitution shown in FIG. 42, similar to the constitution shown in
FIG. 20 (seventh embodiment), sub-seal rings 114 are provided in the first
and second seal rings 62a, 62b, and a spring member 135 is fitted instead
of sub-seal ring 114 in the constitution shown in FIG. 43.
(Fourteenth embodiment)
A fourteenth embodiment is described below while referring to FIG. 44 to
FIG. 48.
This embodiment relates to enhancement of assembling performance of helical
blade compressor having the features of the invention.
That is, in the assembling process of the compression mechanism 3, first,
the seal ring 19 is fitted into the roller 14, and then inserted into the
cylinder 12. In this embodiment, in order to insert smoothly, edges of the
seal ring 19 or cylinder 12 are chamfered 141a to 141d.
In FIG. 44, the inner side edge of the cylinder 12 is chamfered 141a, in
FIG. 45, the seal ring 19 side is chamfered 141b, and in FIG. 46, both the
cylinder 12 side and seal ring 19 are chamfered 141a, 141b.
Instead of chamfering, as shown in FIG. 47, tapering 142 may be also
applied. Or, as shown in FIG. 48, a step 143 may be formed.
Using thus processed seal ring 19 or cylinder 12, the compression mechanism
3 may be assembled as shown in FIGS. 49A and 49B.
FIG. 49A shows a state immediately before insertion of seal ring 19 into
the cylinder 12 together with the roller 14. As shown in FIG. 49B, the
seal ring 19 has a junction 91, and the junction 91 can be dislocated in
the peripheral direction in natural state.
Therefore, when inserting, the seal ring 19 is inserted into the cylinder
12 while contracting in diameter by pressing and compressing in the axial
direction by means of several jigs 146.
At this time, if contraction of the seal ring 19 is not sufficient, it is
properly guided by the action of the chamfered portion 141b, so that
insertion error hardly occurs.
The jigs used for contracting the seal ring 19 may be replaced by 147 shown
in FIGS. 50A and 50B. The jig 147 has a pair of pins 147a, 147b provided
so as to be driven, and the pins 147a, 147b are engaged respectively with
engagement holes 148a, 148b provided in the junction 91 of the seal ring
19, so that the junction 91 can be compressed.
(Fifteenth embodiment)
FIG. 51 is a diagram showing a structural example of a refrigeration cycle
apparatus using the helical blade type compressor of the embodiment as the
compressor.
In the refrigeration cycle apparatus of this embodiment, in particular, the
working refrigerant is a refrigerant of higher condensation or evaporation
pressure, such as HFC system refrigerant R32, R410A or R407C, than R22.
By using the refrigerant high in condensation or evaporation pressure, an
absolute pressure difference between the high pressure side and low
pressure side of the cycle is greater. In such condition, the sealing
performance of high pressure and low pressure in the cylinder tends to be
worse, and the thrust load acting on the roller increases.
However, according to the compressor of the invention, by the use of the
seal ring 19 or 62, the sealing performance is enhanced, and the thrust
load can be adjusted easily, and it is particularly effective when using
such refrigerant.
In particular, R410A is higher than R22 in condensation pressure or
evaporation pressure by about 1.5 times. The use of seal ring 19 or 62 in
such condition is particularly effective means for enhancing the
performance and reliability.
It must be noted, however, that the invention is not limited to the
foregoing first to fifteenth embodiments alone, but may be modified in
various forms within the spirit and range of the invention.
Additional advantages and modifications will readily occur to those skilled
in the art. Therefore, the invention in its broader aspects is not limited
to the specific details and representative embodiments shown and described
herein. Accordingly, various modifications may be made without departing
from the spirit or scope of the general inventive concept as defined by
the appended claims and their equivalents.
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